Varying denier producing pumps and drives



Feb, 4, 1958. w. B.. MILLER 2,821,742

VARYING DENIER PRODUCING PUMPS AND DRIVES Filed Dec. 17, 1952 V 2 Sheeis-Sheet 1 INVENTOR WI LLIAM B. M l L L ER A ORNEYS.

Feb; 4, 1958 w. B. MILLER VARYING DENIER PRODUCING PUMPS AND DRIVES 2 Sheets-Sheet 2 Filed Dec. 17, 1952 INVENTOR. WILLIAM B. MILLER Y I I United States Patent- VARYINGI DENIER' PRODUCINGIUMPS: #DRIVES William 'B.? Miller, Rome,.iGa., assignprto Celanese Cor po -anon orAmeric'a, New York, N. 'Y., a -'cor oration of Delaware ApplicationDeceinber 17,1952; Serial No. 326,469

11 Claims; -(Cl. -18--'-"8) This invention relates to "the production of artificial filaments, yarns orthreads of varying denier,:and"relates more 'particula'ilyto the production of such materialsby the extrusion of spinning solutions through suitable spinning orifices.

Artificial filaments of yarns of varying denier,haviug alternate thick and thin portions, are commonly employed in the manufacture of novelty woven fabri'cs havingtia rough or irregular texture, such as shantung fabrics.

p aszirtz Fatented Feb. 4, 1958 I or the piston away from the delivery'passa'ge produces a thinner'portion in the filaments.

Ina preferred construction, the piston fits closely in the cylinder along substantially the whole length thereof and the reciprocating movement or the piston is such thatattheend of its forward thrust the piston reaches substantiallyto the-delivery passage. This construction minimizes leakage-and also has the desirable feature of expelling substantially all the spinning solution in the cylinderatone stroke. The latter feature is particularly important in-theispinning of viscose spinning solutions,

This rough texture is .due t'o'the presence of "slowr thick portions invthe irregular denieryarn", which may be employed either as the warp or as the weft or both C of the wovenf'abric. Although many devices have been previously proposed tor-producin artificial filaments or yarns of'irr'egul'ar denier, none of these has proved entirely satisfactory, particularly'fo'r use in the produo 'tion of irregular denier regenerat'ed'cellulose"yarns made by the viscose process. For example, such devices have involved unduly handling of'the yarnfhave not been satisfactory for the production of a desirable, sharp change in the denier or the yarn] or have been of -such since any stagnant viscose solution not expelled from the cylinder by the piston would gradually ripen and eventually coagulate in the cylinder.

ln the'preferred construction or this invention, the 'spinning pumphas substantially parallel sides, with "the iifle'ttor the pump andth'e rotating drive shaft for the pump "bein located on one side and the outlet for the pump on the other side. The cylinder block is mounted i on the outlet side or the 'pump with the delivery passage nature that the equipment must be located in the corr'o Y 'sive atmospheres present in certain parts of the viscose spinning process. Also, prior devices havenotbeen adaptable to the limited space-available in the standard machines for spinning artificialfilaments, which machines frequently have hundreds or adjacentspinningpositions for producing hundreds or continuous filaments simul- 'taneously. In addition, the yarns of'irregular deuier made by suchprior devices often yielded woven fa'br-ics in which the slubs, or thick portions; or the yarn were arranged in a definitepat'tern. Such a pattern isgen erally considered to be highly undesirable by the-users of novelt shantung fabrics.

It is an important object of this invention to provide an improved device for producing artificial filaments or yarns of varying denier whichWill bezsubstantially free from these and other disadvantages.

Another object of this invention.is' the'iprovision'ofi a noveldevice-for" producing artificial filaments or yarns of varying: denier, which is easily adapted to'th'e limited space available in standard machines for spinning artificialilfilaments, and which produces a desirable,sharp change in the denier of the filaments or. yarns.

A further object of this invention is to provide anovel device for producing artificial .filamen'ts or yarns v.o'f irregular denier which may be employed 1 asweft yarns for thepro'du ctionrof'woven:fabrics, of normal :conimer cial widths; showing. practicallynot definite .slub patterns;

Other objects of thistinventionwill appearfromrthe following detailed:descriptiontand claims.

The apparatus of this inventiontcomprises..apzconventional" spinning jet, or? 'spinneret'te, :and a spinning! pump :for' supplying solution to theaspinning 'ijet. vThe spinning pump is prov-ided with ia=rotatingt driveshaftaandcan; inlet and an: outlet for the -spinning: solution. :Mountedaonthe spinning pump is aeeylinderoblockhhavinga delivery passage therethrough for delivering spinning solution from or the cylinder block directly connected with the pump outlet. The piston is normally urged out of the cylinder and'away from the delivery passage in the cylinder block by means'of'a spring, mounted around the piston, and by the back pressure of the spinning solution, and is reciprocated by means of a tappe't arm which engages oneend of thepiston. This tappet arm is attached to one end o'fa rocker shaft carried by -a bearing integral. with the cylinder block. At its other end the rocker shaft carries a cam follower provided with a cam follower roller. When the cam follower roller comes incontact with one of the points of the cam, the-motion of *the roller is transmitted from the cam-follower arm to the rockershatt and tappeta-rm and t-hereby forces the piston towards the delivery passage of the cylinder block, thus increasing the pressure of the spinning solution in the delivery passage and producing a sine or thickened por- 'tion in. the :filament or yarn.

' The cam is located on the inlet side of the pump and is-zmounted around the drive shaft 'of the pump. Also mounted around this drive shaft are a cam-gear wheel operativelysconnected with the cam anda pump gear wheel operatively connected with the drive shaft.- Means are'provi'ded .for drivingthe pump-gear wheel at asub- 'stanti'al'ly ccnstantspeed and for driving the eam at .a continuously variable speed, as described below. This continuonsvariation in the speed of the -cam,-added to the fact that the pointsof the cam are spaced at irregular intervalsmrouii'd the periphery of the cam, helps to produce a desirable irregularity in "the's'pac-ings or theslubs of'tlt'e yarns'or filaments.

rlntoneternbodimentof this invention-the ipum'p' gear'and cam jgear; aredriven from a common power input. common power input is transmitted more or less directly to .thepumpgear, while it is transmitted 'to thecanr :gear through a speed changing device, or scrambler, and a gear train, thelatterbeing hereinafter termed primevscrarnbler gearing? lhespeed changing. device includes. a driving rotatingrnember or fscramblei' driver,,provided with a craiik pin, anda driven: rotatingelement mounted onan axis which is eccentric to the axis of rotation of the scrambler driver. The driven element is provided with a radial groove and a block adapted to slide in said groove and to engage the crank pin of the scrambler driver. Rotation of the scrambler driver at a constant speed causes its crank pin to move the sliding block in a circular path around the axis of the scrambler driver, which path is eccentric to the axis of the driven element, so that the sliding block will move back and forth in the radial groove of the driven element. This eccentric motion of the block causes the driven element to rotate at a variable speed with the speed of rotation changing continuously throughout each revolution of the driven element. Thus, one revolution of the driven element may be said to be one cycle of variable speed rotation of that element.

The purpose of the prime scrambler gearing is twofold. First, it functions to establish a velocity pattern of the cam which differs markedly between successive revolutions. In the second place, it provides a relationship between the speed of the cam and the speed of the scrambler so that the scrambler and cam do not regain the same exact phase relationship until a very large amount of yarn has been spun. This produces a maximum irregularity in the spacing of the slubs. This is done by selecting the number of teeth and arrangement of the gears of the prime scrambler gearing so that the cam and driven element cannot become exactly rephased in their original positions until each has made a very large number of revolutions. For example, the gears should be such that the ratio of the speed of the cam to the speed of the driven element may be expressed as a ratio of two large different integral numbers having no common factors, with each of these numbers being desirably above about 5,000. To provide a desirable large variation in the speed of the cam within any single revolution thereof the ratio of the rotational speed of the cam to the rotational speed of the driven element should be within the range of about 0.75:1 to about 1.33:1. For example, a ratio of 7192 complete revolutions of the cam for each 5957 complete revolutions of the driven element is suitable.

Another modification is designed particularly for use where space is extremely limited and where it is desired to apply an individual speed changing device to each spinning pump. In this modification the cam, cam gear wheel and pump gear wheel are mounted around the rotating drive shaft of the pump and, in addition, there is provided a wobble plate mounted around said drive shaft. The wobble plate has a central opening which is engaged by an eccentric hub of the pump gear wheel so that rotation of the pump gear wheel and its eccentric hub causes the wobble plate to oscillate. The pivotal axis for this oscillation is a long pin extending from the wobble plate to the cam gear wheel and passing through an arcuate slot in the cam, the cam being situated between the wobble plate and the cam gear wheel. Means are provided for driving the cam gear wheel at a constant speed. The wobble plate is operatively'connected to the cam by a short pin which is fixed to the wobble plate and fits into a radial slot in the cam. Thus, the motion transmitted to the cam by the wobble plate is a combination of its oscillatory motion about the axis of the long pin and the constant rotational motion of this axis caused by rotation of the cam gear wheel.

Fig. 5 is an elevational view, partly in section, of the modification shown in Fig. 4.

Like reference numerals indicate like parts throughout the several views of the drawings.

In the drawings, reference numeral 10 designates a generally conventional spinning pump, which is a gear pump driven through a drive shaft 11. The gear pump 10 has a flat inlet side 12 and a flat outlet side 13 parallel to said inlet side. Gear pump 10 is provided with an inlet port 14 for receiving spinning solution from an inlet pipe 16 and with an outlet port 17 in side 13, the spinning solution being delivered at a constant rate to the outlet port 17. Attached to the outlet side 13 by any suitable means, such as screws (not shown), is a cylinder block 18 having a delivery passage 19, communicating with the pump outlet port 17 of the gear pump 10 and an inclined piston passage 20 which is at right angles to and communicates with the delivery passage 19. The delivery passage 19 is connected at its exit end 21 to a delivery pipe (not shown) which leads spinning solution directly from said delivery passage to a spinnerette (not shown). A screw plug 22 closes one end of the piston passage 20 and extends into said piston passage down to the intersection of said piston passage with the delivery passage 19. This plug 22 is easily removable when it is desired to clean the piston passage 20. The portion of the piston passage 20 which is not filled by the plug 22 is designated herein as a cylinder 23 and is adapted to receive a long closely fitting cylindrical piston 24 which reciprocates in said cylinder 23. Movement of the piston 24 in the direction away from the delivery passage 19 draws spinning solution from the delivery passage 19 into the cylinder 23 and decreases the pressure on the spinning solution in delivery passage 19, while movement of the piston 24 in the direction towards the delivery passage 19 forces the spinning solution from the cylinder 23, thus increasing the pressure on the spinning solution in said delivery passage.

In the accompanying drawings, which illustrate certain Fig. 4 is an exploded view of a modified arrangement for I driving the spinning pump and the cam, and

The end of the piston 24, extending from the lower end of cylinder 23, is provided with a collar 25 having integral therewith a fiat disk 26, the function of which appears below. Piston 24 is urged from the cylinder 23 by a helical spring 27 encircling piston 24 and engaging, at one end, the collar 25 and, at its other end, a cylindrical extension 28 of the cylinder block 18. If desired, the spring 27 may be of larger diameter so as to fit around the extension 28 and the collar 25 and abut against the main body block 18 and against disk 26. The latter construction provides a somewhat better path for the escape of any leakage of spinning solution which may occur around the piston 24.

Cylinder block 18 is also provided with a relatively long cylindrical bearing 29 extending across and in front of the gear pump 10 from outlet side 13 to inlet side 12. This bearing 29 supports a rocker shaft 31 of such length that it projects from both ends of said bearing. At one end of rocker shaft 31 near collar 25 there is mounted a tappet arm 32 fixed to the rocker shaft 31 by a'tapered pin key 33. Tappet arm 32 is provided with a bracket 34 which has mounted therein an adjustable tappet screw 36 adapted to engage the flat disk 26. The other end of rocker shaft 31 has fixed thereto arm 37, the free end of which carries for free rotation a cam follower 38. The cam follower is adapted to engage a cam 39 having a plurality of irregularly spaced cam points 41, six such points being shown in Fig. 2 of the drawings, with all the distances, or rotational angles, between cam points being different.

Cam 39 is mounted on a hub 42 of a gear wheel 43, and is secured to said gear wheel by means of screws 44. The gear wheel 43 is, in turn, mounted for free rotation on a hollow spindle 45 fixed to the inlet side 12 of the gear pump 10. To space the cam 39 and gear wheel 43 from the gear pump 10 and to provide a broader base for securing the hollow spindle 45 to the inlet side "tein illustrated in Fig. "an input shaft 61, connected to a suitable source of power,

enemas '12 off's'aid ages-r pnntp; ash llbwspihleis presided "with aliange' 4 6. The htillovvsplirdle *45 'fitsebncentrically around the drive shaft 11 ofiih'e pnm'p 10- andcarrie's a pump drive gea fiheel w"indented fer free rotation *onsaid spindle. This gear wheel" 47 drives "the drive shaft 11 thrdug'he plate as-whieh is hired to the gear "wheel 47 b meansbtserevt s w and which is fixed to 'the rectangular and '50 of thedrive shaft 11, which is circular in cross-section.

In operation, rotation of thegear wheel 43 causes rotation of the-cam 39"Which acts= to impart a rocking motion to the rocker shaft 3 1-a'nd thereby to reciprocate the piston 24 in the cylinder 23, thusv'arying the pressure on the spinning solution. The c'ampoints 41 of eam139 are so designed as to ca use 'the piston 24 to move upward rapidly through its entire stroke until 'the'end of the piston 24 reaches the deli-very passage 19, producing a slub on the filaments by the resulting increased pressure on the spinning solution,then*to move downwardly ra idl for a minor ortion "of its stroke, thus-rapidly "releasing the'pressure and terminating'the 'slub, and then to move more slowlyto the lowest position of the piston, thereby allowing further accumulation of solution in the cylinder 23 and producing the thin portions "of the filaments, which thin portions are "considerably longer than t the Slub.

If desired, the length 'of the 'pi'stonst'rokemay be varied by varying the effective length of the arm 31. Thus, the arm "37 may be provided with more than one location, alon its length, for mounting the "roller 38.

The pump drive gear wheel 47 is driven at a substantially constant speed and the cam gear wheel 43 isdriven at a continuously variable speed by a'trans'mission sys- In this transmission system,

carries a pulley 62 and a gear 63 both of which are keyed to the power input shaft 61. The pump drive gear wheel 47 is driven by pulley 62 through a belt 64, a pulley "'66 engaged by said belt, a shaft 67 keyed to'the pulley 66, and a gear 68 keyed to the shaft 67 -and meshing with drive gear wheel 47. The cam gear wheel 43 is driven by the gear 63 on thepo'w'er input shaft 61 through gearing designated as 69 which drives a shaft 71 keyed to ascrarnbler driver 72 connected to a circularscrambler driven element 73, described more fully below. The scrambler driven element is keyed to a shaft 74 operatively connected to a prime scrambler gearing, generally indicated by reference numeral 75, described more fully below. The gearing '75 drives a shaft 76 to which is keyed a 'gear 77 meshing with an idler gear 78 mounted for free rotation on shaft 67 and meshing with the cam gear 43. If desired, shafts 67 and 71 may be driven from separate motors.

'S'cr-a mbler driver 72 is provided 'with a crank pin 79 adapted to engage inan aperture 81 'formed in a sliding b k 82, which is mounted for movement along a' radial groove '83 of'the scrambler driven element '73. The shaft '74, on which the scrambler driven element 73 is mounted, is not coaxial with the shaft 71, to which the "scrambler driver 72 is keyed. Accordingly, the rotation of 'the scrambler driver 72 will cause the sliding block 82 to followa circular path which is concentric with the "axis of rotation 'of scrambler driver 72 but eccentric to the axis of rotation of the scrambler driven element 73, this path being shown in dotted lines on the fa'ce ofthe scrambler driven element"73, so that the sliding block 82 will move back and forth in the radial groove 83. It is readily seen that the rotation of shaft 71 and scrambler driver 72 at a constant speed will cause scrambler driven element 73, and its connected shaft 74, to rotate at a continuously va in'g speed. When sliding block 82 is farthest from the center of rotation er scrambler driven element 73*the rotational speed of the scrambler driven ""efit '73 'wil'l its leviest'va-lue'w l'e 'wh elderw reeves elosest te' the'eenter-etrottweiler 6 said erambler driven element the' 'rotatienal speed eithe latter "will be -'at its highest value.

As stated-Ahe prime scrambler gearing is connected withthescrannbler driven element 73 through shaft 74 and bperates the earn 39 through gear'wheel 43'whi'ch isrotated throughidler gear 78,-ge'a r 77 and shaft 76. The prime scrambler gearing 75 establishes a cycle et Tt'atiOflOf hh'e (z 3 111 39 Which is 6111 OfPh'a'SetO' 'a large emenewith the cycle of rotation of the scrambler driven element 73. This is done by providing an arrangement of gears so that the 'cain' 39 and driven element 73 cannot become exactly 're rhased in their original positions u'n'til each-has made a very large number of revolutions, that is, by selecting gears wherein the number 0f gear teeth is 'such't-hat the ratio of the speed of the gear 43 t0 the speed Of the scrambler driven element 73 may he expressed 3% a IElfiO Of 'tW'O large dilte'rent ififegl'iil numbers having "110 "common fa'C tOt, 'With each Of-the's'e numbers being above about 5000, and-with the ratio of these numbers being within the range of about 0.7 511 to a out 1.33:1.

Figs-4 and 5 illustrate a modification of the arrangerne'nt of the cam gear and pump gear. In this modificatienahellow spindle 85, which fits 'over the pump drive shaft 11 and is attached to the inlet side 12 of the gear pump ih, is of the same shape as, but somewhat shorter than, the hollow spindle 45 illustrated in Fig. '1. The pump gear wheel 86, driven by a gear wheel 87, fits over "the hollow spindle 85 and is secured to the pump drive shaft 11 by means of a plate 88 attached to the pump gear wheel-8'6 and fixed to the rectangular end 50 of the pum drive shaft 11. Pump gear wheel 86 is provided with an integral hub 89 having a cylindrical inner'surface 91, fitting over the hollow spindle 8'5 and concentric with circular drive shaft 11, and a cylindrical outer surface 92 which is parallel to and eccentric to inner surface 91. Fitting over this eccentric outer surface 92 is a cir- 'c'ular wobble plate 93 having a centrally located opening 94 in the shape of a rectangle whose narrower, transverse, sides are of the same length as the diameter of the eccentric cylindrical outer surface 92 of the hub 89. This wobble plate 93 is provided with a short cylindrical pin 96 and a long cylindrical pin 97, both pins being fixed to said wobble plate and extending in a direction away from the pump gear wheel 86. These pins 96 and 97 are both located at diametrically opposed points along a diameter of the wobble plate 93, which diameter runs along the long axis of the rectangular opening '94. The short'pin "96 fits into a radial slot 98 in a cam 99, the width of the radial slot 98 being about the same as the diameter of the short pin 96 and its length being considerably greater than the diameter of the pin 96. The long pin "97 fits through a relatively long arcuate slot 1'01in the cam 99, the Width of the slot 101 being about the same asthe diameter of the pin '97, and extends into a hole 102 in a cam gear wheel 103. The cam gear wheel 103, which meshes with a driving gear wheel 104, is provided with "a cylindrical hub 106 and is mounted for free rotation on the hollow spindle 85. This cylindrical hub 1'06 serves as a mounting for the cam 99, which is provided with a central circular opening 107 so that it fits over said cylindrical hub 106 and may be rotated thereon. The cam 99 is also provided on its circumference with a multiplicity of irregularly spaced points 108, allot the distances er rotational angles between earn points being dilterent. 3 lindr'ical hollo'w spindle s5, hub 106 of cam gear-wheel 1'03, circular opening 107 of cam 99 and the inner surface 91 'of hub 89 of pump gear wheel 86 are all concentric with pump drive shaft 11, and all eccentric to the outer surface 92 'of hub 89 of pump gear 86.

The operation of the modification shown'in Figs. 4"a'nd 5 may be easily understood, by 'firstexa'mining what would happen if the cam gear wheel 103'were'held "in fixedp'os'ition and not allowed to rotates/hen the pump g ar wheel e6 rotates. Ittlreeam-gearwheel'itll is'held statiena'r'y,

the rotation of the pump gear wheel 86 will drive the pump drive shaft 11 and at the same time cause the wobble plate 93 to rock back and forth due to the action of the eccentric outer surface 92 of the pump gear wheel hub 89. The pivotal axis for the rocking of the wobble plate 93 will be the axis of the long pin 97 journalled in the hole 102 of the cam gear wheel 103. This rocking movement of wobble plate 93 will be transmitted through short pin 96 to cam 99 and cause a corresponding rocking movement of said cam. In actual operation, of course, the cam gear wheel 103 is not stationary but is driven by the driving gear wheel 104. This causes a rotation of the hole 102 of cam gear wheel 103 and therefore a rotation of the pivotal axis of the wobble plate 93 and a rotation of the cam 99. Accordingly, the motion of the cam will be the algebraic sum of the rotational motion imparted from the cam gear wheel 103 and the rocking or oscillating motion imparted from the eccentric outer surface 92, so that the cam will rotate around its axis at a continuously varying rate. I

In practice, the number of teeth on the various gears 86, 87, 103 and 104 are selected so that the rotational speeds of the cam gear wheel 103 and the pump drive gear wheel 86 are different. By selection of gears one can insure that the cycle of rotation of the cam gear wheel 103 is out of phase with the cycle of rotation of the pump gear wheel 86 to a large extent. If desired, cam gear wheel 103 and pump gear wheel 86 may be driven by the arrangement illustrated in Fig. 3, with cam gear wheel 103 engaging idler gear 78 and pump gear wheel 103 engaging gear 68 of Fig. 3. In such a construction elements 103, 99, 93 and 86 of Fig. 4 would replace elements 39, 43 and 47 of Fig. 3.

While this invention has been described more particularly in connection with the spinning of viscose solutions it is equally applicable to the production of artificial filaments or yarns of irregular denier using other spinning liquids. Examples of such suitable spinning liquids are cuprammonium solutions of cellulose, solutions of cellulose derivatives, e. g. nitrocellulose, cellulose acetate, cel lulose propionate or ethyl cellulose, solutions of filamentforming synthetic high polymers, e. g. polyacrylonitrile, vinyl chloride copolymers or acrylonitrile copolymers, solutions of filament-forming proteins, e. g. zein or casein, and molten filament-forming high polymers such as nylon .or other synthetic liner polyamides.

It is to be understood that the foregoing detailed description is given merely by way of illustration and that many variations may be made therein without departing from the spirit of my invention.

Having described my invention, what I desire to secure by Letters Patent is:

1. In apparatus for producing artificial filaments having variations in denier along the length thereof by extruding a spinning liquid, means, including a spinning pump, for extruding said spinning liquid, said spinning pump having substantially parallel sides with an inlet and rotating drive shaft on one side and an outlet for spinning liquid on the other side, a cylinder block mounted on the outlet side of said spinning pump, said cylinder block having a delivery passage therethrough directly connected with said outlet for delivering spinning liquid from said outlet, a cylinder communicating with said delivery passage, a reciprocating piston closely fitting in said cylinder along substantially the whole length of said cylinder, the end of said piston reaching substantially to the delivery passage at one extreme of its reciprocating movement, spring means around said piston for urging said piston out of said cylinder, a cam, a wheel for driving said cam, a wheel for driving said drive shaft, said cam and wheel being mounted around said drive shaft with said cam wheel rotating independently of said drive shaft wheel, a tappet arm adapted to engage said piston, a cam follower arm having means adapted to engage said cam, a rocking shaft operatively connecting said tappet arm and said cam follower arm, means for driving said drive shaft wheel at a constant speed and means for driving said cam at a continuously variable speed.

2. In apparatus for producing artificial filaments having variations in denier along the length thereof by extruding a spinning liquid, means, including a spinning pump, for extruding said spinning liquid under pressure, means cooperating With said spinning pump for intermittently varying the denier of the filaments, a rotary cam for operating said means and means for rotating said cam at a continuously varying speed, said cam rotating means including a driving rotating member, an eccentric driven rotating member, said members being joined by connecting means mounted for movement in a circular path around the axes of both of said rotating members, said circular path being concentric with one of said axes and eccentric to the other of said axes.

3. In apparatus for producing artificial filaments having variations in denier along the length thereof by extruding a spinning liquid, means, including a spinning pump, for extruding said spinning liquid under pressure, means cooperating with said spinning pump for intermittently varying the denier of the filaments, a rotary cam for operating said means and means for rotating said cam at a continuously varying speed, said means for rotating said cam including a driving rotating member, an eccentric driven rotating member, said members being joined by a crank pin mounted for movement in a circular path around the axes of both of said rotating members, said circular path being concentric with one of said axes and eccentric to the other of said axes, the construction and arrangement being such that the velocity pattern of the cam is changed markedly in successive revolutions of said cam.

4. In apparatus for producing artificial filaments having variations in denier along the length thereof by extruding a spinning liquid, means, including a spinning pump, for extruding said spinning liquid under pressure, means cooperating with said spinning pump for intermittently varying the denier of the filaments, a rotary cam for operating said means and means for rotating said cam at a continuously varying speed, said means for rotating said cam including a speed changing means receiving a rotary motion at constant speed and transmitting a rotary action at continuously variable speed to a rotary driven member, and means for connecting said driven member to said cam, said connecting means being so constructed and arranged that said driven member makes a large integral number of complete revolutions in the same time period as said cam makes a different large integral number of complete revolutions, said integral numbers having no common factor.

5. In apparatus for producing artificial filaments having variations in denier along the length thereof by extruding a spinning liquid, means, including a spinning pump, for extruding said spinning liquid under pressure, means cooperating with said spinning pump for intermittently varying the denier of the filaments, a rotary cam for operating said means and means for rotating said cam at a continuously varying speed, said means for rotating said cam including a speed changing means receiving a rotary motion at constant speed and transmitting a rotary motion at continuously variable speed to a rotary driven member, and gearing for connecting said driven member to said cam, said gearing being so constructed and arranged that said driven member makes a large integral number of complete revolutions in the same period as said cam makes a different large integral number of complete revolutions, said integral numbers having no common factor.

6. In apparatus for producing artificial filaments having variations in denier along the length thereof by extruding a spinning liquid, means, including a spinning pump, for extruding said spinning liquid under pressure, means cooperating with said spinning pump for intermittently varying the denier of the filaments, a rotary cam for operating said means andmeans for rotating said cam at a continuously varying speed, said means for rotating said cam including a speed changing means receiving a rotary motion at constant speed and transmitting a rotary motion at continuously variable speed to a rotary driven member, and gearing for connecting said driven member to said cam, said gearing being so constructed and arranged that said driven member makes a large integral number of complete revolutions in the same time period as said cam makes a different large integral number of complete revolutions, said integral numbers having no common factor, each of said numbers being in excess of about 5000 and the ratio of the number of revolutions of said cam to the number of revolutions of said driven member being Within the range of about 0.75:1 to about 1.33:1.

7. In apparatus for producing artificial filaments having variations in denier along the length thereof by extruding a spinning liquid, means, including a spinning pump, for extruding said spinning liquid under pressure, means cooperating with said spinning pump for intermittently varying the pressure of the spinning liquid supplied to said spinning jet, a rotary cam for operating said means and means for rotating said cam at a continuously varying speed, said means for rotating said cam including a driving rotating member, an eccentric driven rotating member, said members being joined by a crank pin mounted for movement in a circular path around the axes of both of said rotating members, said circular path being concentric with one of said axes and eccentric to the other of said axes, and gearing for connecting said driven member and said cam, said gearing being so constructed and arranged that said driven member makes a large integral number of complete revolutions in the same time period as said cam makes different large integral number of complete revolutions, said integral numbers having no common factor and each of said numbers being in excess of about 5000 and the ratio of the number of revolutions of said cam to the number of revolutions of said driven member being within the range of about 0.75:1 to about 1.33:1.

8. In apparatus for producing artificial filaments having variations in denier along the length thereof by extruding a spinning liquid, means, including a spinning pump, for extruding said spinning liquid, said spinning pump having a rotating drive shaft, means for intermittently varying the denier of the filaments, a rotary cam mounted around 10 said drive shaft for operating said means and means mounted around said drive shaft for rotating said cam at a continuously variable speed.

9. In apparatus for producing artificial filaments having variations in denier along the length thereof by extruding a spinning liquid, means, including a spinning pump, for extruding said spinning liquid under pressure, means cooperating with said spinning pump for intermittently varying the denier of the filaments, a rotary cam for operating said means, means rotating at a constant speed for driving said spinning pump, means for rotating said cam, and means, operated by said means for driving said spinning pump, for continuously varying the rotational speed of said cam.

10. A device for producing a continuously variable rotary motion of a rotary member, comprising two wheels each adapted to be driven, a wobble plate and a rotary cam, said two wheels and said rotary cam being mounted concentrically, an eccentric hub on one of said wheels and engaging in a central opening in said wobble plate for oscillating said wobble plate during the rotation of one of said wheels, an operative connection between said wobble plate and the second of said wheels for transmitting the rotary motion of said second wheel to said wobble plate and means for transmitting the motion of wobble plate to the rotary cam.

11. A device for producing a continuously variable rotary motion of a rotary member, comprising two wheels each adapted to be driven, a wobble plate and a rotary cam, said two Wheels and said rotary cam being mounted concentrically, an eccentric hub on one of said wheels and engaging in a central opening in said wobble plate for oscillating said Wobble plate during the rotation of one of said wheels, a pin, connecting said Wobble plate and the second of said wheels and passing through a slot in said rotary cam, for transmitting the rotary motion of said second wheel to said wobble plate and a second pin attached to said wobble plate and engaging in a radial slot in said rotary cam for transmitting the motion of said wobble plate to said rotary cam.

References Cited in the file of this patent UNITED STATES PATENTS 1,678,398 Lange July 24, 1928 1,770,297 Bussmann July 8, 1930 2,391,973 Hunter Ian. 1, 1946 

